CN110582658B - Continuously variable transmission and transmission belt - Google Patents
Continuously variable transmission and transmission belt Download PDFInfo
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- CN110582658B CN110582658B CN201880029766.9A CN201880029766A CN110582658B CN 110582658 B CN110582658 B CN 110582658B CN 201880029766 A CN201880029766 A CN 201880029766A CN 110582658 B CN110582658 B CN 110582658B
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- pulley
- pair
- continuously variable
- variable transmission
- ring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G5/00—V-belts, i.e. belts of tapered cross-section
- F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
- F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
- F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
Abstract
A continuously variable transmission includes a drive belt having a plurality of cells and a ring, the cells including: a main body portion having a saddle-shaped surface; and a pair of stay portions extending from the body portion so as to be positioned on both sides in the width direction of the saddle surface, wherein the loop is disposed between the pair of stay portions of the plurality of cells, and the belt is wound around the V-shaped grooves of the first pulley and the second pulley, and wherein when one of the first pulley and the second pulley has the smallest groove width, at least a portion of the loop wound around the one of the first pulley and the second pulley in the thickness direction protrudes radially outward beyond an outermost periphery of a surface of the V-shaped groove of the one of the first pulley and the second pulley.
Description
Technical Field
The present invention relates to a continuously variable transmission including a transmission belt having a plurality of single bodies and a ring binding the single bodies into an annular shape, and a transmission belt.
Background
Conventionally, there is known a continuously variable transmission including a metal V-belt composed of a metal endless belt (belt strap), a plurality of metal blocks attached to the belt, and an endless belt-like holding belt for holding the metal blocks in a state of being attached to the belt (see, for example, patent document 1). Each metal block of the metal V-belt has a belt-disposing groove opened upward through which a belt passes on an upper surface, and mounting grooves for mounting and holding the belt are formed on both inner side surfaces in the belt-disposing groove. The holding belt has a flat-plate-like cross section having the same width over the entire circumference, and an opening for easily elastically deforming the flat plate surface into an arc shape when inserted into the belt-disposing groove is formed in at least one position of the flat plate surface of the holding belt. The holding belt is assembled to each metal block by inserting both ends thereof into the mounting grooves, and covers the belt passing through the belt disposition groove in a state where the elastic deformation is released and the cross section in the width direction is restored to a flat plate shape.
Documents of the prior art
Patent document
Patent document 1: JP-A-3-72139
Disclosure of Invention
In the continuously variable transmission including the metal V-belt as described above, the transmission ratio range can be further increased by increasing the maximum winding radius of the metal V-belt with respect to the drive pulley and the driven pulley. However, the invention described in patent document 1 aims to easily attach the metal block to the metal belt, and there is no specific means for further enlarging the transmission gear ratio range in patent document 1.
It is therefore a primary object of the present invention to further increase the maximum winding radius of the drive belt and thereby further increase the speed ratio range of the continuously variable transmission.
The continuously variable transmission of the present invention includes: a first pulley on a driving side, a second pulley on a driven side, and a drive belt having a plurality of cells and rings, the cells comprising: a main body portion having a saddle-shaped surface; and a pair of stay portions extending from the body portion so as to be positioned on both sides of the saddle surface in the width direction, wherein the ring is disposed between the pair of stay portions of the plurality of cells, and the belt is wound around the V-shaped grooves of the first pulley and the second pulley, and wherein when one of the first pulley and the second pulley has the smallest groove width, at least a portion of the ring wound around the one of the first pulley and the second pulley in the thickness direction protrudes radially outward beyond an outermost periphery of a surface of the V-shaped groove of the one of the first pulley and the second pulley.
In this continuously variable transmission, when power is transmitted from the first pulley to the second pulley via the transmission belt, the pair of strut parts can restrict the ring from falling off from the single body. Thus, when the groove width of one of the first pulley and the second pulley is minimized, at least a portion of the ring wound around the one of the first pulley and the second pulley in the thickness direction can be made to protrude radially outward beyond the outermost periphery of the surface of the V-shaped groove of the one of the first pulley and the second pulley. As a result, the maximum winding radius of the transmission belt with respect to the first pulley and the second pulley can be further increased, and therefore, the transmission ratio range of the continuously variable transmission can be further increased.
Drawings
Fig. 1 is a schematic configuration diagram showing an example of a continuously variable transmission according to the present invention.
Fig. 2 is a partial sectional view showing a main portion of the continuously variable transmission of the present invention.
Fig. 3 is a side view of a single body included in the transmission belt of the continuously variable transmission of the present invention.
Fig. 4 is a schematic diagram for explaining the operation of the continuously variable transmission of the present invention.
Fig. 5 is a schematic diagram for explaining the operation of the continuously variable transmission of the present invention.
Detailed Description
Next, a mode for carrying out the present invention will be described with reference to the drawings.
Fig. 1 is a schematic configuration diagram showing a Continuously Variable Transmission (CVT) 1 of the present invention. A continuously variable transmission 1 shown in the figure is mounted on a vehicle, and the continuously variable transmission 1 includes: a primary shaft (first shaft) 2 as a driving-side rotation shaft; a primary pulley (first pulley) 3 provided on the primary shaft 2; a secondary shaft (first shaft) 4 as a driven-side rotation shaft disposed parallel to the primary shaft 2; a secondary pulley (second pulley) 5 provided on the secondary shaft 4; and a belt 10. As shown in the drawing, the transmission belt 10 is wound around a pulley groove (V-shaped groove) of the primary pulley 3 and a pulley groove (V-shaped groove) of the secondary pulley 5.
The primary shaft 2 is coupled to an input shaft (not shown) connected to a power generation source, which is referred to as an engine (internal combustion engine) of a vehicle, via a forward/reverse switching mechanism (not shown). The primary pulley 3 includes: a fixed sheave 3a formed integrally with the primary shaft 2; and a movable sheave 3b supported by the primary shaft 2 via a ball spline or the like so as to be slidable in the axial direction. In addition, the secondary pulley 5 includes: a fixed sheave 5a formed integrally with the secondary shaft 4; and a movable sheave 5b supported by the secondary shaft 4 via a ball spline or the like so as to be slidable in the axial direction and urged in the axial direction by a return spring 8.
Moreover, the continuously variable transmission 1 includes: a primary cylinder 6 as a hydraulic actuator for changing a groove width of the primary pulley 3; the secondary cylinder 7 as a hydraulic actuator changes the groove width of the secondary pulley 5. The primary cylinder 6 is formed behind the movable sheave 3b of the primary pulley 3, and the secondary cylinder 7 is formed behind the movable sheave 5b of the secondary pulley 5. In order to change the groove widths of the primary pulley 3 and the secondary pulley 5, working oil is supplied to the primary cylinder 6 and the secondary cylinder 7 from an unillustrated oil pressure control device. The secondary shaft 4 is coupled to drive wheels (all not shown) of the vehicle via a gear mechanism, a differential gear, and a drive shaft.
In the present embodiment, a stepped portion is formed at an end portion (left end portion in fig. 1) of the primary shaft 2 on the side opposite to the engine side. An annular end plate 65 is interposed between the stepped portion and the primary piston 60 of the primary cylinder 6 so as to be able to contact an end portion (left end portion in fig. 1) of the movable sheave 3b of the primary pulley 3 on the side opposite to the engine side. Further, a stopper portion 2s is formed in the primary shaft 2 so as to be able to abut against an end portion of the spline teeth 3s formed on the inner peripheral surface of the movable sheave 3b on the fixed sheave 3a side.
Fig. 2 is a partial cross-sectional view showing the belt 10. As shown in the drawing, the belt 10 includes: a single laminated ring 12 configured by laminating a plurality of (for example, 9 in the present embodiment) elastically deformable ring members 11 in the thickness direction (ring radial direction); a retainer ring 15; and a plurality of (for example, several hundred) cells 20 arranged (bundled) annularly along the inner peripheral surface of the stack ring 12.
The plurality of ring members 11 constituting the laminated ring 12 are each an elastically deformable member cut out from a steel plate Drum (Drum), and are processed to have substantially the same thickness and different circumferential lengths. The retainer ring 15 is an elastically deformable member cut out from a drum made of, for example, steel plate, and has a thickness substantially the same as or thinner than that of the ring member 11. In addition, the slinger 15 has an inner circumference that is longer than the outer circumference of the outermost ring member 11o of the laminated ring 12. Thus, in a state where the stack ring 12 and the retainer ring 15 are concentrically arranged (a non-load state where tension is not applied), as shown in fig. 2, an annular gap is formed between the outer peripheral surface of the outermost ring member 11o and the inner peripheral surface of the retainer ring 15.
Each of the cells 20 is a member punched out of a steel plate by press working, for example, and as shown in fig. 2, each of the cells 20 has: a main body 21 extending horizontally in the figure; a pair of column parts 22 extending in the same direction from both ends of the body part 21; and a single ring housing portion (recess) 23 that is formed between the pair of column portions 22 so as to be divided to open toward the free end side of each column portion 22. The pair of column portions 22 extend from both sides in the width direction of the saddle surface 23s that is the bottom surface of the ring housing portion 23 to the outside in the radial direction of the laminated ring 12 (the direction from the inner circumferential side to the outer circumferential side of the transmission belt 10 (laminated ring 12), that is, upward in the drawing), and a hook portion 22f that protrudes in the width direction of the saddle surface 23s is formed at the free end portion of each column portion 22.
The pair of hook portions 22f are slightly longer than the width of the stack ring 12 (ring member 11), and face each other with a space shorter than the width of the stopper ring 15. Each of the strut parts 22 of the unit 20 has a flat inner surface 22i inclined so as to be spaced apart from the saddle surface 23s as it goes outward in the radial direction of the laminated ring 12, and a concave curved surface (for example, a concave cylindrical surface) smoothly continuing between the saddle surface 23s and the inner surface 22i of each strut part 22 is formed therebetween.
As shown in fig. 2, the stacked rings 12 are arranged in the ring housing 23, and the saddle-shaped surface 23s of the ring housing 23 is in contact with the inner circumferential surface of the ring member 11 on the innermost layer, which is the stacked rings 12. The saddle-shaped surface 23s has a bilaterally symmetric convex curved surface shape (convex shape) that is gently inclined downward in the figure toward the widthwise outer side with the widthwise central portion as the top portion T. Thus, a centripetal force toward the top T is applied to the laminated ring 12 by friction with the saddle surfaces 23s, and the laminated ring 12 can be centered. However, the saddle surface 23s may include a plurality of convex curved surfaces that curve outward in the radial direction of the laminated ring 12.
Then, the elastically deformed retainer ring 15 is fitted into the ring housing 23 from between the pair of hook portions 22f of each unit 20. The stopper ring 15 is disposed between the outer peripheral surface of the outermost ring member 11o of the laminated ring 12 and the hook portion 22f of each unit 20, surrounds the laminated ring 12, and regulates, together with the pair of column portions 22, the detachment of each unit 20 from the laminated ring 12 or the detachment of the laminated ring 12 from the unit 20. Thereby, the plurality of cells 20 are bundled (arranged) in a ring shape along the inner peripheral surface of the stack ring 12. In the present embodiment, the retainer ring 15 is formed with a single or multiple openings (elongated holes), not shown, so that the retainer ring 15 can be easily elastically deformed, thereby ensuring the ease of assembly into the single body 20.
As shown in fig. 2, a pair of rocking edge portions (contact regions) 25, non-contact portions 27, tapered surfaces (inclined surfaces) 21s, and a single protrusion (depression) 21p are formed on the front surface (one surface) of the single body 20. The pair of rocking edges 25 are formed on the front surface of the single body 20 at intervals in the width direction of the saddle surface 23s so as to straddle the corresponding strut member 22 and the body portion 21. In addition, the non-contact portion 27 is formed in the middle of the pair of rocking edge portions 25 in the above-described width direction. The tapered surface 21s is formed on the front surface (one surface) of the main body portion 21 so as to extend from the non-contact portion 27 and the pair of rocking edge portions 25 toward the inner peripheral side (lower side in fig. 2) of the belt opposite to the projecting direction of each pillar portion 22. The projection 21p projects from the tapered surface 21s at the center in the width direction of the front surface of the body 21.
In the present embodiment, as shown in fig. 3, the front surface of the cell 20 (mainly, the front surface of the column portion 22) and the back surface (the other surface) of the cell 20 on the outer circumferential side of the belt with respect to the rocking edge portion 25 and the non-contact portion 27 are formed flat, and the column portion 22 of the cell 20 has a constant thickness te. As shown in fig. 3, the tapered surface 21s on the inner peripheral side of the belt (lower side in fig. 2 and 3) of each rocking edge portion 25 and non-contact portion 27 approaches the back surface (back surface) as it moves away from the strut portion 22 (as it moves toward the inner peripheral side of the belt). A recessed portion 21r is formed on the rear surface of the cell 20 (main body portion 21) so as to be positioned on the rear surface side of the projection 21p. When the belt 10 is assembled, the projections 21p of the adjacent cells 20 are loosely fitted into the recessed portions 21r.
Each rocking edge portion 25 is a convex curved surface in a short belt shape, and in the present embodiment, is formed as a cylindrical surface (curved surface) having a predetermined radius of curvature and having a width in the radial direction. Each of the rocking edge portions 25 includes a contact line 25c (see fig. 3) that brings the adjacent cells 20 into contact with each other and serves as a rotation fulcrum of both, and the position of the contact line 25c varies within the range of the rocking edge portion 25 in accordance with the gear ratio γ of the continuously variable transmission 1. In the present embodiment, the radially outer end of the rocking edge portion 25 (the upper side in the figure, i.e., the pillar portion 22 side) is located radially outward of the saddle surface 23s, and the radially inner end of the rocking edge portion 25 (the lower side in the figure, i.e., the tapered surface 21s side) is located radially inward of the saddle surface 23 s.
The non-contact portion 27 is a belt-like recessed portion that is open on the saddle surface 23s, extends in the width direction along the saddle surface 23s, and is formed on the front surface (one surface) of the main body portion 21 so as to separate the pair of rocking edges 25. The surface (bottom surface) of the non-contact portion 27 is recessed toward the back surface side from the surface of each rocking edge portion 25, and thus the thickness of the saddle surface 23s is smaller than the thickness te of the strut portion 22. The corner of the non-contact portion 27 (concave portion) and the edge of the main body 21 defining the non-contact portion 27 are processed into a rounded shape by chamfering or the like. By forming such non-contact portions 27 in each element 20, the contact with the adjacent element 20 at a portion other than the rocking edge portion 25, that is, the contact between the adjacent element 20 and the non-contact portion 27 can be favorably suppressed in the transmission belt 10. As a result, it is possible to suppress the load from the central portion in the width direction of the cell 20 on which a large moment acts from being applied to the adjacent cell 20 to deform the cell 20, and it is possible to further improve the durability of each cell 20.
The single body 20 has a pair of side surfaces 20s formed so as to be spaced apart from each other from the inner circumferential side of the laminated ring 12 toward the outer circumferential side (the outer side in the radial direction of the laminated ring 12). As shown in fig. 2, each side surface 20s includes: a first side surface 20sa located on the pillar portion 22 side, i.e., on the opposite side (outer side) of the inner surface 22i of the pillar portion 22; the second side surface 20sb is formed continuously with the first side surface 20sa, and is located radially inward of the stack ring 12 than the first side surface 20 sa. In the present embodiment, the pair of first side surfaces 20sa and the pair of second side surfaces 20sb are formed so as to be separated from each other as they go outward in the radial direction of the laminated ring 12. This can ensure the strength of each column part 22 satisfactorily.
As shown in fig. 2, the angle θ b formed by the pair of second side surfaces 20sb is set to be substantially equal to (slightly larger than the design value of the opening angle θ 0 in the present embodiment) the opening angle θ 0 of the pulley grooves of the primary pulley 3 and the secondary pulley 5, and the angle θ a formed by the pair of first side surfaces 20sa is set to be smaller than the angle θ b formed by the pair of second side surfaces 20 sb. Thus, the second side surface 20sb of the single body 20 comes into frictional contact with the pulley groove of the primary pulley 3 and the pulley groove surface of the secondary pulley 5, receives the clamping pressure from the pulleys 3 and 5, and serves as a torque transmission surface (side surface) for transmitting torque from the primary pulley 3 to the secondary pulley 5 by frictional force. In contrast, the pair of first side surfaces 20sa does not substantially contact the pulley groove surfaces when torque is transmitted from the primary pulley 3 to the secondary pulley 5 via the transmission belt 10. In the present embodiment, on the surface of each second side surface 20sb, irregularities (a plurality of grooves), not shown, for retaining working oil for lubricating and cooling the contact portions between each element 20 and the primary pulley 3 and the secondary pulley 5 are formed.
Next, the operation of the continuously variable transmission 1 will be described with reference to fig. 2, 4, and 5.
When a vehicle equipped with the continuously variable transmission 1 travels, a hydraulic pressure corresponding to a target speed ratio of the continuously variable transmission 1 determined based on an accelerator opening degree (throttle opening degree) of the vehicle, a vehicle speed, and an engine speed is supplied to the primary cylinder 6 from a hydraulic control device (not shown). Further, the hydraulic pressure regulated so as to suppress the slip of the transmission belt 10 is supplied from the hydraulic control device to the sub cylinder 7. This allows the torque transmitted from the engine (power generation source) of the vehicle to the primary shaft 2 via the input shaft and the forward/reverse switching mechanism to be continuously changed in speed and output to the secondary shaft 4.
Further, at the time of starting the vehicle or the like, the movable sheave 3b of the primary pulley 3 is separated from the fixed sheave 3a by adjusting the hydraulic pressures of the primary cylinder 6 and the secondary cylinder 7, and the end portion (the left end portion in fig. 1) of the movable sheave 3b on the side opposite to the engine side is brought into contact with the end plate 65, whereby the movement of the movable sheave 3b relative to the primary shaft 2 in the direction away from the fixed sheave 3a is regulated. Accordingly, when the end of the movable sheave 3b abuts against the end plate 65, the width of the pulley groove of the primary pulley 3 is maximized, and the transmission ratio γ of the continuously variable transmission 1 is maximized by setting the width of the pulley groove of the secondary pulley 5 to be minimized by the transmission belt 10.
Here, in the continuously variable transmission 1, even if the ring housing portion 23 of the single unit 20 protrudes radially outward beyond the outer peripheries of the primary pulley 3 and the secondary pulley 5 when torque is transmitted from the primary pulley 3 to the secondary pulley 5 by the transmission belt 10, the pair of stay portions 22 and the stopper ring 15 can restrict the stacked ring 12 from falling off from the single unit 20. Based on this, the specifications of the continuously variable transmission 1 (the outer diameters of the pulleys 3, 5, the circumferential length of the belt 10, and the like) are set such that, when the width of the pulley groove of the primary pulley 3 becomes maximum, the width of the pulley groove of the secondary pulley 5 becomes minimum, and the transmission ratio γ becomes maximum, as shown in fig. 2 and 4, substantially the entire laminated ring 12 wound around the secondary pulley 5 in the thickness direction protrudes radially outward from the outermost periphery X of the pulley groove surface of the secondary pulley 5 (the fixed sheave 5a and the movable sheave 5 b). This can further increase the maximum winding radius of the transmission belt 10 with respect to the secondary pulley 5, and thus can further increase the gear ratio range of the continuously variable transmission 1.
On the other hand, when the end portion on the fixed sheave 3a side of the spline teeth 3s formed on the inner peripheral surface of the movable sheave 3b is brought into contact with the stopper portion 2s formed on the primary shaft 2 by adjusting the oil pressures of the primary cylinder 6 and the secondary cylinder 7, the movement of the movable sheave 3b relative to the primary shaft 2 in the direction approaching the fixed sheave 3a is restricted. When the end of the spline tooth 3s of the movable sheave 3b abuts against the stopper portion 2s of the primary shaft 2, the width of the pulley groove of the primary pulley 3 becomes minimum, and the width of the pulley groove of the secondary pulley 5 is set to be maximum by the belt 10, thereby minimizing the transmission ratio γ of the continuously variable transmission 1. Further, the continuously variable transmission 1 of the present embodiment is set to have a specification (outer diameter of the pulleys 3 and 5, circumferential length of the belt 10, etc.) such that when the width of the pulley groove of the primary pulley 3 becomes minimum, the width of the pulley groove of the secondary pulley 5 becomes maximum, and the transmission ratio γ becomes minimum, the laminated ring 12 wound around the primary pulley 3 projects radially outward from the outermost circumference X of the surface of the pulley groove of the primary pulley 3 (the fixed sheave 3a and the movable sheave 3 b) substantially as a whole, as shown in fig. 2 and 5. This can further increase the maximum winding radius of the transmission belt 10 with respect to the primary pulley 3, and thus can further increase the gear ratio range of the continuously variable transmission 1.
In this way, in the continuously variable transmission 1, when the width of the pulley groove of one of the primary pulley 3 and the secondary pulley 5 is the smallest, substantially the entire lamination ring 12 wound around one of the primary pulley 3 and the secondary pulley 5 in the thickness direction protrudes radially outward beyond the outermost circumference X of the surface of the pulley groove of the primary pulley 3 and the secondary pulley 5. As a result, the maximum winding radius of the transmission belt with respect to the primary pulley 3 and the secondary pulley 5 can be further increased, and therefore, the gear ratio range of the continuously variable transmission 1 can be further increased. In the present embodiment, the surfaces of the pulley grooves of the primary pulley 3 and the secondary pulley 5 are conical surfaces, and the outermost circumference X of the surfaces of the pulley grooves is a boundary between the surface (conical surface) of the pulley groove and a chamfered portion formed at the edge portion of the fixed sheaves 3a and 5a and the movable sheaves 3b and 5 b.
In the present embodiment, the continuously variable transmission 1 is configured such that, when the width of the pulley groove of the primary pulley 3 is maximized, the width of the pulley groove of the secondary pulley 5 is minimized, and the transmission ratio γ is maximized, the contact line 25c of the cells 20 wound around the secondary pulley 5 is not positioned radially outward of the outermost periphery X of the pulley groove surface of the secondary pulley 5, but is preferably positioned on a circumference having the same diameter as the outermost periphery X or an actual outermost periphery set radially inward of the outermost periphery X. Further, when the width of the pulley groove of the primary pulley 3 is minimum, the width of the pulley groove of the secondary pulley 5 is maximum, and the transmission ratio γ is minimum, the continuously variable transmission 1 is configured such that the contact line 25c of the cells 20 wound around the primary pulley 3 is not located radially outward of the outermost circumference X of the pulley groove surface of the primary pulley 3, and is preferably located on a circumference having the same diameter as the outermost circumference X or an actual outermost circumference set slightly radially inward of the outermost circumference X.
That is, in the continuously variable transmission 1, when the width of the pulley groove of one of the primary pulley 3 and the secondary pulley 5 is the smallest, the boundary between the surface on the outer peripheral side of the belt (mainly, the front surface of the stay portion 22) and the swinging edge portion 25 of the single body 20 does not exceed the outermost periphery X and is located radially outward. This makes it possible to further increase the maximum winding radius of the transmission belt 10 with respect to the secondary pulley 5 by bringing the contact line 25c between the cells 20 radially outward, and to reduce the moment acting in the pitch direction of the cell 20 pressed by the adjacent cell 20 via the contact line 25c (see the arrow in fig. 3).
Further, in the continuously variable transmission 1, the side surface 20s of each element 20 includes: a first side surface 20sa that is not substantially in contact with a surface of the pulley groove when torque is transmitted from the primary pulley 3 to the secondary pulley 5 using the transmission belt 10; and a second side surface 20sb serving as a torque transmission surface that receives a clamping pressure from the primary pulley 3 and the secondary pulley 5 and transmits torque by a frictional force. Accordingly, even if the speed ratio γ of the continuously variable transmission 1 is changed, the contact area between each single unit 20 and the surface of the pulley groove can be kept constant, and therefore, deterioration of the operation of each single unit 20 due to a change in the load center can be suppressed.
Further, in the continuously variable transmission 1 described above, the end portion of the movable sheave 3b abuts against the end plate 65 fixed to the primary shaft 2, and the movement of the movable sheave 3b relative to the primary shaft 2 in the direction away from the fixed sheave 3a is restricted, whereby the width of the pulley groove of the secondary pulley 5 is set to be minimum via the transmission belt 10, but the present invention is not limited thereto. That is, the width of the pulley groove of the secondary pulley 5 may be set to be minimum by bringing the end portion of the movable sheave 5b into contact with a stopper portion, not shown, formed on the secondary shaft 4, and restricting the movement of the movable sheave 5b relative to the secondary shaft 4 in the direction approaching the fixed sheave 5 a. Further, the hydraulic pressure supplied to the primary cylinder 6 and the secondary cylinder 7 may be adjusted to set the positions of the movable sheaves 3b and 5b at predetermined limit positions in the continuously variable transmission 1, thereby minimizing the width of the pulley groove of the secondary pulley 5.
In the continuously variable transmission 1, the end of the spline tooth 3s of the movable sheave 3b abuts against the stopper 2s formed on the primary shaft 2, and the movement of the movable sheave 3b relative to the primary shaft 2 in the direction approaching the fixed sheave 3a is restricted, whereby the width of the pulley groove of the primary pulley 3 is set to be minimum, but the present invention is not limited thereto. That is, the width of the pulley groove of the primary pulley 3 may be set to the minimum by bringing the end portion of the movable sheave 5b into contact with an end plate (or a secondary piston), not shown, fixed to the secondary shaft 4, and restricting the movement of the movable sheave 5b relative to the secondary shaft 4 in the direction away from the fixed sheave 5 a. Further, the hydraulic pressure supplied to the primary cylinder 6 and the secondary cylinder 7 may be adjusted to set the positions of the movable sheaves 3b and 5b at predetermined limit positions in the continuously variable transmission 1, thereby minimizing the width of the pulley groove of the primary pulley 3.
In the continuously variable transmission 1, when the width of the pulley groove of one of the primary pulley 3 and the secondary pulley 5 is the smallest, the substantially entire laminated ring 12 wound around one of the primary pulley 3 and the secondary pulley 5 in the thickness direction protrudes radially outward beyond the outermost periphery X of the surface of the pulley groove of one of the primary pulley 3 and the secondary pulley 5, but the present invention is not limited thereto. That is, when the width of the pulley groove of one of the primary pulley 3 and the secondary pulley 5 is the smallest, at least the outermost ring member 11o of the laminated ring 12 wound around one of the primary pulley 3 and the secondary pulley 5 may protrude radially outward from the outermost circumference X, and the entire laminated ring 12 may protrude radially outward from the outermost circumference X. When the width of the pulley groove of one of the primary pulley 3 and the secondary pulley 5 is the smallest, the ring member 11 may protrude radially outward from the outermost periphery X by about half of the outer periphery of the laminated ring 12 wound around the one of the primary pulley 3 and the secondary pulley 5.
In the continuously variable transmission 1, the width of the pulley groove of the primary pulley 3 is the smallest when the transmission gear ratio γ is the smallest, but the width of the pulley groove of the primary pulley 3 may be the smallest when the transmission gear ratio γ of the continuously variable transmission 1 is not the smallest. In the continuously variable transmission 1, the width of the pulley groove of the secondary pulley 5 is the smallest when the transmission ratio γ is the largest, but the width of the pulley groove of the secondary pulley 5 may be the smallest when the transmission ratio γ of the continuously variable transmission 1 is not the largest. In these cases, the continuously variable transmission 1 may be configured such that the primary shaft 2 and the secondary shaft 4 are selectively coupled to the input shaft, and the primary shaft 2 and the secondary shaft 4 are selectively coupled to a drive shaft of the vehicle.
In the transmission belt 10 of the continuously variable transmission 1, the pair of hook portions 22f are provided in each unit 20, and the retainer ring 15 is disposed between the laminated ring 12 and the hook portions 22f of the plurality of unit 20. That is, the hook 22f may be omitted from each unit 20 of the belt 10, or the stopper ring 15 may be omitted from the belt 10.
As described above, the continuously variable transmission (1) according to the present invention includes: a first pulley (3) on a driving side, a second pulley (5) on a driven side, and a transmission belt (10), wherein the transmission belt (10) has a plurality of single bodies (20) and rings (12), and the single bodies (20) include: a main body part (21) having a saddle-shaped surface (23 s); and a pair of strut members (22) extending from the body portion (21) so as to be positioned on both sides in the width direction of the saddle surface (23 s), wherein the ring (12) is disposed between the pair of strut members (22) of the plurality of cells (20), and the transmission belt (10) is wound around the V-shaped grooves of the first pulley (3) and the second pulley (5), and wherein, when one of the first pulley (3) and the second pulley (5) has the smallest groove width, at least a portion of the ring (12) wound around one of the first pulley (3) and the second pulley (5) in the thickness direction protrudes radially outward beyond an outermost circumference (X) of the surface of the V-shaped groove of one of the first pulley (3) and the second pulley (5).
In the continuously variable transmission of the present invention, when power is transmitted from the first pulley to the second pulley by the transmission belt, the pair of stay portions can restrict the ring from falling off from the single body. Thus, when the groove width of one of the first pulley and the second pulley is minimized, at least a portion of the ring wound around one of the first pulley and the second pulley in the thickness direction can be made to protrude radially outward beyond the outermost periphery of the surface of the V-shaped groove of one of the first pulley and the second pulley. As a result, the maximum winding radius of the transmission belt with respect to the first pulley and the second pulley can be further increased, and therefore, the transmission ratio range of the continuously variable transmission can be further increased.
In addition, the first pulley (3) may include: a fixed sheave (3 a) integrated with the first shaft (2); and a movable sheave (3 b) supported by the primary shaft (2) so as to be freely slidable in the axial direction, and the groove width of the secondary pulley (5) can be made minimum also when the movement of the movable sheave (3 b) relative to the primary shaft (2) in the direction away from the fixed sheave (3 a) is restricted. In this case, the movable sheave (3 b) may be partially abutted against a part of the primary shaft (2) or a member (65) fixed to the primary shaft (2) to restrict the movement of the movable sheave (3 b) relative to the primary shaft (2) in a direction away from the fixed sheave (3 a).
Furthermore, the first pulley (3) may include: a fixed sheave (3 a) integrated with the first shaft (2); and a movable sheave (3 b) supported by the primary shaft (2) so as to be freely slidable in an axial direction, and a groove width of the primary pulley (3) may also become minimum when movement of the movable sheave (3 b) with respect to the primary shaft (2) in a direction approaching the fixed sheave (3 a) is restricted. In this case, the movement of the movable sheave (3 b) relative to the primary shaft (2) in the direction approaching the fixed sheave (3 a) may be restricted by a part (3 s) of the movable sheave (3 b) of the primary pulley (3) abutting against a part (2 s) of the primary shaft (2).
Further, when the transmission ratio (γ) of the continuously variable transmission (1) is maximized, the groove width of the second pulley (5) may be minimized. This can further increase the gear ratio range of the continuously variable transmission.
Further, when the transmission ratio (γ) of the continuously variable transmission (1) is minimum, the groove width of the first pulley (3) may also become minimum. This can further increase the gear ratio range of the continuously variable transmission.
The cells (20) may include a rocking edge portion (25), the rocking edge portion (25) may be formed on one of the front and back surfaces of the cells (20), and may include a contact line (25 c) that serves as a fulcrum for rotation of the adjacent cells (20) by contacting each other, and when the groove width of one of the first pulley (3) and the second pulley (5) is the smallest, the contact line (25 c) between the cells (20) wound around one of the first pulley (3) and the second pulley (5) may be located radially inward of an outermost circumference (X) of a surface of a V-shaped groove of one of the first pulley (3) and the second pulley (5). This makes it possible to further increase the maximum winding radius of the transmission belt with respect to the first pulley and the second pulley by making the contact line between the cells more radially outward, and to reduce the moment acting in the pitch direction of the cell pressed by the adjacent cell via the contact line.
The single body (20) may include a pair of torque transmission surfaces (20 sb) that contact the surfaces of the V-shaped grooves, and the torque transmission surfaces (20 sb) may not protrude radially outward from the outermost periphery (X) of the surfaces of the V-shaped grooves.
Further, the single body (20) may include a pair of side surfaces (20 s), the pair of side surfaces (20 s) being formed so as to be separated from each other from the inner circumferential side toward the outer circumferential side of the ring (12), and the pair of side surfaces (20 s) may include: a first side surface (20 sa) provided to the column section (22); and a second side surface (20 sb) that is formed so as to be continuous with the first side surface (20 sa), wherein an angle (θ b) formed by the pair of second side surfaces (20 sb) may be substantially equal to an opening angle (θ 0) of the V-shaped grooves of the first pulley (3) and the second pulley (5) on the inner peripheral side of the first side surface (20 sa), and an angle (θ a) formed by the pair of first side surfaces (20 sa) may be smaller than the angle (θ b) formed by the pair of second side surfaces (20 sb). When power is transmitted from the first pulley to the second pulley by the belt having the single bodies, the second side surface of the side surface of each single body can be brought into contact with the surface of the V-shaped groove, and the first side surface on the side of the support column can be prevented from being brought into contact with the surface of the V-shaped groove. Accordingly, even if the gear ratio of the continuously variable transmission is changed, the contact area between each unit and the surface of the V-shaped groove can be kept constant, and therefore, deterioration of the operation of each unit due to a change in the load center can be suppressed.
The plurality of single bodies (20) may further include a pair of hook portions (22 f), the pair of hook portions (22 f) protruding from the free end portion of the pillar portion (22) in the width direction of the saddle surface (23 s) and facing each other, and the transmission belt (10) may further include a stopper ring (15) disposed between the ring (12) and the hook portions (22 f) of the plurality of single bodies (20).
The outermost periphery (X) of the surface of the V-shaped groove may be a boundary between the surface of the V-shaped groove and a chamfered portion formed at an edge portion of the first pulley or the second pulley (3, 3a, 3b, 5a, 5 b).
The present invention is a power transmission belt (10) having a plurality of single bodies (20) and a ring (12), wherein the single bodies (20) include: a main body part (21) having a saddle surface (23 s); and a pair of strut members (22) extending from the body portion (21) so as to be positioned on both sides of the saddle surface (23 s) in the width direction, wherein the ring (12) is disposed between the pair of strut members (22) of the plurality of cells (20), and wherein the belt (10) is wound around V-shaped grooves of a first pulley (3) and a second pulley (5) of a continuously variable transmission (1), and wherein, when one of the first pulley (3) and the second pulley (5) has the smallest groove width, at least a portion of the ring (12) wound around one of the first pulley (3) and the second pulley (5) in the thickness direction protrudes radially outward beyond an outermost circumference (X) of a surface of the V-shaped groove of one of the first pulley (3) and the second pulley (5).
In the continuously variable transmission including the belt, the maximum winding radius of the belt with respect to the first pulley and the second pulley can be further increased, and therefore, the gear ratio range of the continuously variable transmission can be further increased.
The present invention is not limited to the above-described embodiments, and it is apparent that various modifications can be made within the scope of the invention. The above embodiment is only a specific embodiment of the invention described in the summary of the invention, and is not intended to limit the invention described in the summary of the invention.
Industrial applicability
The present invention can be applied to the manufacturing industry of continuously variable transmissions and transmission belts.
Claims (13)
1. A continuously variable transmission comprising: a first pulley on a driving side, a second pulley on a driven side, and a drive belt having a plurality of cells and rings, the cells comprising: a main body part having a saddle surface; and a pair of strut parts extending from the body part so as to be positioned on both sides in the width direction of the saddle surface, wherein the loop is disposed between the pair of strut parts of the plurality of single bodies, and the belt is wound around the V-shaped grooves of the first pulley and the second pulley,
when one of the first pulley and the second pulley has a minimum groove width, at least a portion of the ring wound around the one of the first pulley and the second pulley in the thickness direction protrudes radially outward from an outermost periphery of a surface of the V-shaped groove of the one of the first pulley and the second pulley,
the single body comprises a swinging edge part which is formed on one of the front surface and the back surface of the single body and comprises a contact line which makes the adjacent single bodies contact with each other and becomes a fulcrum of the rotation of the two single bodies,
when the groove width of one of the first pulley and the second pulley is the smallest, the contact line between the single bodies wound around the one of the first pulley and the second pulley is located radially inward of the outermost periphery of the surface of the V-shaped groove of the one of the first pulley and the second pulley.
2. The continuously variable transmission of claim 1,
the first pulley includes: a fixed sheave integrated with the first shaft; and a movable sheave supported by the first shaft so as to be freely slidable in an axial direction,
when the movement of the movable sheave relative to the primary shaft in the direction away from the fixed sheave is restricted, the groove width of the secondary pulley becomes minimum.
3. The continuously variable transmission of claim 2,
when a part of the movable sheave abuts against a part of the primary shaft or a member fixed to the primary shaft, the movable sheave is restricted from moving in a direction away from the fixed sheave with respect to the primary shaft.
4. The continuously variable transmission according to any one of claims 1 to 3,
the first pulley includes: a fixed sheave integrated with the first shaft; and a movable sheave supported by the first shaft so as to be freely slidable in an axial direction,
when the movement of the movable sheave with respect to the primary shaft in the direction approaching the fixed sheave is restricted, the groove width of the primary pulley becomes minimum.
5. The continuously variable transmission according to claim 4,
when a part of the movable sheave of the primary pulley abuts against a part of the primary shaft, the movable sheave is restricted from moving in a direction approaching the fixed sheave with respect to the primary shaft.
6. The continuously variable transmission according to any one of claims 1 to 3,
when the transmission ratio of the continuously variable transmission is at a maximum, the groove width of the second pulley becomes at a minimum.
7. The continuously variable transmission according to any one of claims 1 to 3,
when the transmission ratio of the continuously variable transmission is minimum, the groove width of the first pulley becomes minimum.
8. The continuously variable transmission according to any one of claims 1 to 3,
the single body includes a pair of torque transmitting surfaces in contact with the surfaces of the V-shaped groove,
the torque transmission surface does not protrude radially outward from the outermost periphery of the surface of the V-shaped groove.
9. A continuously variable transmission comprising: a first pulley on a driving side, a second pulley on a driven side, and a drive belt having a plurality of cells and rings, the cells comprising: a main body part having a saddle surface; and a pair of strut parts extending from the body part so as to be positioned on both sides in the width direction of the saddle surface, wherein the loop is disposed between the pair of strut parts of the plurality of single bodies, and the belt is wound around the V-shaped grooves of the first pulley and the second pulley,
when one of the first pulley and the second pulley has a minimum groove width, at least a portion of the ring wound around the one of the first pulley and the second pulley in the thickness direction protrudes radially outward from an outermost periphery of a surface of the V-shaped groove of the one of the first pulley and the second pulley,
the single body includes a pair of side surfaces formed to be separated from each other as going from an inner circumferential side toward an outer circumferential side of the ring,
the pair of side surfaces respectively include: a first side surface provided to the pillar portion; and a second side surface formed continuously with the first side surface and located closer to the inner peripheral side than the first side surface,
the angle formed by the pair of second side surfaces is substantially equal to the opening angle of the V-shaped grooves of the first pulley and the second pulley, and the angle formed by the pair of first side surfaces is smaller than the angle formed by the pair of second side surfaces.
10. The continuously variable transmission according to claim 9,
the plurality of single bodies further include a pair of hook portions that protrude from the free end portion of the column portion in the width direction of the saddle surface and face each other,
the drive belt also has a stopper ring disposed between the ring and the hook portions of the plurality of cells.
11. The continuously variable transmission according to claim 9 or 10,
the outermost periphery of the surface of the V-shaped groove is a boundary between the surface of the V-shaped groove and a chamfered portion formed at an edge portion of the first pulley or the second pulley.
12. A power transmission belt having a plurality of cells and rings, the cells comprising: a main body portion having a saddle-shaped surface; and a pair of strut parts extending from the body part so as to be positioned on both sides in the width direction of the saddle surface, wherein the ring is disposed between the pair of strut parts of the plurality of single bodies, and the transmission belt is wound around V-shaped grooves of a first pulley and a second pulley of the continuously variable transmission,
when one of the first pulley and the second pulley has a minimum groove width, at least a portion of the ring wound around the one of the first pulley and the second pulley in the thickness direction protrudes radially outward from an outermost periphery of a surface of the V-shaped groove of the one of the first pulley and the second pulley,
the single body comprises a swinging edge part which is formed on one of the front surface and the back surface of the single body and comprises a contact line which makes the adjacent single bodies contact with each other and becomes a fulcrum of the rotation of the two single bodies,
when the groove width of one of the first pulley and the second pulley is the smallest, the contact line between the single bodies wound around the one of the first pulley and the second pulley is located radially inward of the outermost periphery of the surface of the V-shaped groove of the one of the first pulley and the second pulley.
13. A power transmission belt having a plurality of cells and rings, the cells comprising: a main body portion having a saddle-shaped surface; and a pair of strut parts extending from the body part so as to be positioned on both sides in the width direction of the saddle surface, wherein the ring is disposed between the pair of strut parts of the plurality of single bodies, and the transmission belt is wound around V-shaped grooves of a first pulley and a second pulley of the continuously variable transmission,
wherein at least a part of the loop wound around one of the first pulley and the second pulley in the thickness direction protrudes radially outward beyond an outermost circumference of a surface of the V-shaped groove of the one of the first pulley and the second pulley when the groove width of the one of the first pulley and the second pulley is the smallest,
the single body includes a pair of side surfaces formed to be separated from each other as going from an inner circumferential side toward an outer circumferential side of the ring,
the pair of side surfaces respectively include: a first side surface provided to the pillar portion; and a second side surface formed continuously with the first side surface and located closer to the inner peripheral side than the first side surface,
the angle formed by the pair of second side surfaces is substantially equal to the opening angle of the V-shaped grooves of the first pulley and the second pulley, and the angle formed by the pair of first side surfaces is smaller than the angle formed by the pair of second side surfaces.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017-097349 | 2017-05-16 | ||
| JP2017097349A JP6747377B2 (en) | 2017-05-16 | 2017-05-16 | Continuously variable transmission and transmission belt |
| PCT/JP2018/018604 WO2018212140A1 (en) | 2017-05-16 | 2018-05-14 | Continuously variable transmission and motion transfer belt |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110582658A CN110582658A (en) | 2019-12-17 |
| CN110582658B true CN110582658B (en) | 2022-11-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880029766.9A Active CN110582658B (en) | 2017-05-16 | 2018-05-14 | Continuously variable transmission and transmission belt |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US11466757B2 (en) |
| JP (1) | JP6747377B2 (en) |
| CN (1) | CN110582658B (en) |
| WO (1) | WO2018212140A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US11454299B2 (en) * | 2017-06-02 | 2022-09-27 | Aisin Corporation | Transmission belt element and transmission belt |
| JP6740962B2 (en) * | 2017-06-09 | 2020-08-19 | アイシン・エィ・ダブリュ株式会社 | Transmission belts and elements for transmission belts |
| JP6787494B2 (en) * | 2017-08-14 | 2020-11-18 | アイシン・エィ・ダブリュ株式会社 | Transmission belt element and transmission belt |
| CN116877451B (en) * | 2023-09-06 | 2023-12-08 | 福建华电邵武能源有限公司 | Speed regulating device of slurry circulating pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002168305A (en) * | 2000-11-30 | 2002-06-14 | Mitsubishi Motors Corp | Element for continuously variable transmission belt and continuously variable transmission belt |
| JP2008240959A (en) * | 2007-03-28 | 2008-10-09 | Toyota Motor Corp | Belt for continuously variable transmission, and belt-type continuously variable transmission |
| CN102144110A (en) * | 2009-11-20 | 2011-08-03 | 丰田自动车株式会社 | Compressed trasmission belt |
| JP2012127510A (en) * | 2012-03-30 | 2012-07-05 | Toyota Motor Corp | Belt type continuously variable transmission |
| WO2015177372A1 (en) * | 2014-05-22 | 2015-11-26 | Robert Bosch Gmbh | Drive belt for a continuously variable transmission with generally v-shaped transverse members |
Family Cites Families (39)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3824867A (en) * | 1972-12-07 | 1974-07-23 | Mcculloch Corp | Multi-stage control for torque converters in engine driven vehicles |
| US3979963A (en) * | 1975-06-09 | 1976-09-14 | Goettl Adam D | Adjustable V belt pulley |
| US4061047A (en) * | 1976-09-20 | 1977-12-06 | Deere & Company | Pulley half mounting of variable speed pulley |
| IT1197513B (en) * | 1979-10-26 | 1988-11-30 | S I R A Societe Ind Ricerche A | METAL BELT FOR POWER TRANSMISSION |
| JPS5740150A (en) * | 1980-08-22 | 1982-03-05 | Nippon Denso Co Ltd | Power transmission device |
| FR2492031B1 (en) * | 1980-10-09 | 1986-03-07 | Valeo | SPEED VARIATOR PULLEY |
| FR2510701B1 (en) * | 1981-07-31 | 1986-03-28 | Valeo | PULLEY WITH FLANGES WITH VARIABLE GAP, IN PARTICULAR FOR SPEED VARIATOR, PARTICULARLY FOR MOTOR VEHICLE |
| FR2516622B1 (en) * | 1981-11-18 | 1987-04-17 | Valeo | SPEED VARIATOR PULLEY |
| IT1216897B (en) * | 1987-02-27 | 1990-03-14 | Piaggio & C Spa | BELT TRANSMISSION COMPLEX FOR MOTOR VEHICLES, EQUIPPED WITH ENGINE STARTING DEVICE. |
| FR2618511B1 (en) * | 1987-07-23 | 1992-04-10 | Valeo | SPEED VARIATOR PULLEY |
| US4925432A (en) * | 1987-09-25 | 1990-05-15 | Honda Giken Kogyo Kabushiki Kaisha | Belt-type continuously variable transmission and engine speed control device therefore |
| JPH0723643Y2 (en) * | 1989-11-16 | 1995-05-31 | 本田技研工業株式会社 | Metal V belt |
| JPH0738749Y2 (en) * | 1991-04-25 | 1995-09-06 | 有限会社マツオエンジニアリング | Drive belt for continuously variable transmission |
| US5378199A (en) * | 1994-02-04 | 1995-01-03 | Tong Yuan Design & Development Co., Ltd. | Automatic retrieving structure of sliding transmission disk of motorcycle automatic transmission |
| DE19743675A1 (en) * | 1996-10-08 | 1998-04-09 | Luk Getriebe Systeme Gmbh | Steplessly variable power transmission |
| GB2323416B (en) * | 1997-03-15 | 2001-08-01 | Gkn Technology Ltd | Pulley of variable effective diameter |
| DE19946336B4 (en) * | 1998-10-02 | 2013-04-25 | Schaeffler Technologies AG & Co. KG | Continuously adjustable belt drive |
| DE10022846B4 (en) * | 1999-05-17 | 2013-03-28 | Schaeffler Technologies AG & Co. KG | transmission |
| JP3709971B2 (en) * | 2000-03-07 | 2005-10-26 | 本田技研工業株式会社 | V-belt automatic transmission for vehicles |
| JP2002054690A (en) * | 2000-08-07 | 2002-02-20 | Honda Motor Co Ltd | Belt for continuously variable transmission |
| JP4656856B2 (en) * | 2004-04-26 | 2011-03-23 | 本田技研工業株式会社 | V-belt type automatic transmission |
| US20050272540A1 (en) * | 2004-05-03 | 2005-12-08 | Starkey John M | Coaxial electrical actuator for continuously variable transmission |
| US20060089218A1 (en) * | 2004-10-27 | 2006-04-27 | Aeon Motor Co., Ltd. | Large torque diverting device for an engine transmission system |
| ATE475035T1 (en) * | 2005-11-08 | 2010-08-15 | Bosch Gmbh Robert | TRANSMISSION WITH PULLEYS AND DRIVE BELT |
| JP2007211914A (en) * | 2006-02-10 | 2007-08-23 | Jtekt Corp | Method for applying pretension of power transmission chain, pretension applying device used for the method, and power transmission device |
| US7980972B1 (en) * | 2006-05-01 | 2011-07-19 | Purdue Research Foundation | Roller variator for actuating continuously variable transmissions |
| JP4840654B2 (en) * | 2006-08-04 | 2011-12-21 | 株式会社ジェイテクト | Power transmission chain, method for manufacturing power transmission member of power transmission chain, and power transmission device |
| JP2008196562A (en) * | 2007-02-09 | 2008-08-28 | Yamaha Motor Co Ltd | Power unit and straddle-type vehicle |
| JP5474049B2 (en) * | 2008-04-29 | 2014-04-16 | シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | Conical disc-type wound transmission |
| NL1035388C2 (en) * | 2008-05-02 | 2009-11-03 | Bosch Gmbh Robert | Transmission with bombed pulley discs and a driving belt. |
| WO2012035624A1 (en) * | 2010-09-15 | 2012-03-22 | トヨタ自動車株式会社 | Belt-type continuously variable transmission for vehicle |
| FR2966543B1 (en) * | 2010-10-25 | 2013-06-07 | France Reducteurs | PULLEY FOR BELT TRANSMISSION DEVICE, IN PARTICULAR FOR BELT SPEED DRIVE, AND BELT SPEED DRIVE INCORPORATING SUCH PULLEY |
| US20130079182A1 (en) * | 2011-09-23 | 2013-03-28 | Briggs & Stratton Corporation | Pulley system for outdoor power equipment |
| RU2014115217A (en) * | 2011-10-21 | 2015-11-27 | Тойота Дзидося Кабусики Кайся | MECHANISM WITH A PULLEY FOR A VALVE-FREE VEHICLE TRANSMISSION FOR A VEHICLE |
| DE112013003466T5 (en) * | 2012-07-06 | 2015-03-26 | Honda Motor Co., Ltd. | Element for metallic belt |
| NL1040165C2 (en) * | 2013-04-15 | 2014-10-16 | Gear Chain Ind Bv | SERIAL CONTINUOUS VARIABLE TRANSMISSION. |
| US9958044B2 (en) * | 2013-08-09 | 2018-05-01 | Honda Motor Co., Ltd. | Power transmission switching mechanism and transmission |
| US10648554B2 (en) * | 2014-09-02 | 2020-05-12 | Polaris Industries Inc. | Continuously variable transmission |
| NL1041121B1 (en) * | 2014-12-23 | 2016-10-11 | Bosch Gmbh Robert | A pushbelt for a continuously variable transmission and a transmission provided therewith. |
-
2017
- 2017-05-16 JP JP2017097349A patent/JP6747377B2/en active Active
-
2018
- 2018-05-14 CN CN201880029766.9A patent/CN110582658B/en active Active
- 2018-05-14 US US16/606,086 patent/US11466757B2/en active Active
- 2018-05-14 WO PCT/JP2018/018604 patent/WO2018212140A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002168305A (en) * | 2000-11-30 | 2002-06-14 | Mitsubishi Motors Corp | Element for continuously variable transmission belt and continuously variable transmission belt |
| JP2008240959A (en) * | 2007-03-28 | 2008-10-09 | Toyota Motor Corp | Belt for continuously variable transmission, and belt-type continuously variable transmission |
| CN102144110A (en) * | 2009-11-20 | 2011-08-03 | 丰田自动车株式会社 | Compressed trasmission belt |
| JP2012127510A (en) * | 2012-03-30 | 2012-07-05 | Toyota Motor Corp | Belt type continuously variable transmission |
| WO2015177372A1 (en) * | 2014-05-22 | 2015-11-26 | Robert Bosch Gmbh | Drive belt for a continuously variable transmission with generally v-shaped transverse members |
Also Published As
| Publication number | Publication date |
|---|---|
| US20210148439A1 (en) | 2021-05-20 |
| US11466757B2 (en) | 2022-10-11 |
| CN110582658A (en) | 2019-12-17 |
| JP6747377B2 (en) | 2020-08-26 |
| JP2018194070A (en) | 2018-12-06 |
| WO2018212140A1 (en) | 2018-11-22 |
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